JPH0317388A - Automatic propulsion type impact excavator - Google Patents

Abstract

PURPOSE: To continuously regulate advancing speed and the number of impacts by mounting a drive spring between a drive motor and the rear end of an impact piston. CONSTITUTION: While an impact piston 1 is making one complete rotation in the clockwise direction as seen from a drive shaft 11, the piston 1 is screwed back against a drive spring 17 by an axial distance between the front end and rear end 14 of a guide groove 4. When a guide element 12 projecting radially inward from a housing wall 16 reaches the rear end 14 of the guide groove 4, the spring 17 causes the piston 1 to advance quickly and press against the colliding surface 15 of an impact head 18. Further, the guide element 12 axially passes through the return range 4, 2 of the guide groove 4 from the rear end 14 to the front end 13.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a self-propelled impact excavator, particularly for soil drilling, in which an impact impulse is applied by an impact piston attached to the propulsion side of a cylindrical housing. The percussion piston is capable of driving a pulsatile reciprocating stroke by means of an energy carrier that can be introduced into the device. [Prior art] German Patent No. 2157259 (Special Publication No. 184-1984)
No. 86) was equipped with an impact point (impact head) held within a cylindrical housing and an impact piston that reciprocated within the housing. Air-powered impact excavators are known. The machine's automatically controlled piston applies periodic shocks to a movable shock peak. Under the influence of the impact, the impact point, which is supported by the housing via a compression spring, moves back and forth into the soil, and finally, when its stroke is exhausted, it pulls in the housing. However, on the other hand, machines are known in which the impact point is not movable but is a fixed component of the housing. A machine of this type is described in German Patent Application No. 2105229. Impact excavators of the above-mentioned type are particularly useful for laying utility pipes, such as water supply and drainage, power or telephone lines, for example under roads or footpaths, without having to excavate the road surface or footpath for this purpose. In this case, the impact excavator moves through the soil, displacing and compacting the soil as it moves forward, creating a tunnel into which utility pipes can be inserted without any problems. At its rear end, the percussion excavator can have a connection or joint for securing a subsequent tube. Alternatively, the pipe to be laid can be pulled in with a towline inserted into the tunnel. In the percussion excavator known from DE 21 57 259, the percussion energy is provided by impinging compressed air on the percussion piston. Machines must be supplied with lubricant during operation. This is done by connecting a spray refueling machine to the compressed air supply pipe.
At the same time, particular attention is paid to the determination of oil mist and the adapted use of specific oil qualities, even at different temperatures. For example, in winter, the compressed air is heated by a separate additional heat exchanger to avoid condensation and freezing, thereby avoiding breakdowns. The pressure and quantity of the working medium compressed air should be carefully maintained so that the possibility of damage due to overcharging of the material is excluded. Depending on the pressure value of the pneumatic energy carrier required to achieve the required impact energy, certain limits are set that can significantly influence the number of impacts. These difficulties may appear in some cases when the machine is used as a haikuhammer on very different soil types, such as soils that are contaminated with stones to a greater or lesser extent. Furthermore, it is impossible to implement individual impacts based on a set schedule, for example, when an earth removal hammer is driven into the soil. When there are difficulties in the soil condition, for example, when there is a mixture of rocks, the air-driven impact excavator, which operates with six reciprocating impact points, may be forced to deviate from its operating direction when a stronger obstacle appears. be. [Problem to be solved by the invention] The present invention is based on the problem of presenting a self-propelled impact excavator of the type mentioned at the beginning, which is improved and further developed compared to the state of the art. There is. The machine must be able to drill through rock-containing soil, rock, and hard soil by impact drilling without deviating from the set working direction, and the forward speed and number of impacts must be controlled steplessly using simple means. It must be adjustable and it must be possible to achieve individual impacts without problems, for example when penetrating into the earth.

[Means for solving the problem] The solution to the above problem is a self-propelled shock of the type mentioned at the beginning with or without a movable shock peak! In the J excavator, a spring that periodically tensions and relaxes is used to drive the impact piston. The spring is preferably tensioned by a pneumatically or hydraulically driven motor. The impact U excavator according to the invention has a rotary drive and at least one curve drive which can be driven thereby, the percussion piston having a helical guide groove or helical guide surface as part of the curve drive. It can be formed. In the impact excavator constructed according to the invention, the number of impacts can advantageously be adjusted steplessly via the rotational speed of the rotary drive. This is especially advantageous when the machine is used as an earth removal hammer in a variety of soil types. Due to the low rotational speed of the rotary drive and the individual impacts, this machine can penetrate into the soil much more easily than previously known earth removal hammers. In addition, the percussion drilling machine can simultaneously operate as a percussion drilling machine, for example when the percussion head is connected via a drive shaft or a trailing shaft to a rotating percussion piston. This advantageously achieves that even rock-contaminated rocks do not pose any problems due to the percussion rotation action of the percussion excavator. In that case, the impact head can be equipped with a rock drilling cap to improve its effectiveness in stony soils. The machine can also be equipped with an obliquely cut head in order to be able to advance in a curved manner into the soil in accordance with the technical teachings of DE 30 27 990. On the other hand, linear progression can be achieved by targeted rotational movements in obliquely cut heads of this type. When the rotational motion is interrupted, the machine is controlled in a specific direction according to the inclined surface of the head. The motor is preferably designed as a hydraulic motor and can be connected respectively to an inlet pipe and an outlet pipe for the hydraulic energy carrier, preferably pressurized water. The hydraulic drive system of the motor is given priority because it has a minimum volume structure, can produce high torque, and can be operated at a stepless and predetermined rotation speed within the rotation speed range. The use of pressurized water instead of pressurized oil is further advantageous as it avoids any negative environmental effects due to oil escape. However, the preference for hydraulic drives and the use of pressurized water as the working medium does not preclude the adoption of other hydraulic, pneumatic or electric energy carriers for motor drives.

According to a further proposal, a rotary drive with a moke located outside the machine can be coupled in a rotationally power-transmissible manner to the curved drive via a preferably flexible transmission shaft.

In one embodiment, the rotary drive has a drive shaft located in the center line of the housing, which is rotatably coupled to the motor or transmission shaft on the one hand and to the curved drive in a rotary coupling with an axial play on the other hand. It is designed to engage.

The percussion piston is thus both rotated and translated via a drive shaft by a drive motor which can be driven hydraulically, pneumatically or electrically. This can be achieved, for example, by other proposals in which the percussion piston is connected to the drive shaft, on the one hand in a rotary connection and on the other hand, freely axially, and cut into its cylindrical circumference in a helical manner with the pitch of a thread. This is achieved by forming and arranging a guide element projecting radially inwardly from the housing wall to engage the guide well. In this embodiment, the guide groove has a helical region over an angle of approximately 360° and a region of a return groove connecting its front and rear ends, the latter essentially straight axially or steeply at a slight angle. It is formed into an inclined spiral. In this case, the impact piston has its end opposite the impact surface at 6
It is supported by a drive spring that is provided to act as an energy storage part during its preparatory retreat stroke. During the cooperation of these elements of the curved drive, the guide element is at the curved tip of the groove at the beginning of the rotation of the impact piston, and as the rotation progresses, the guide element passes through the helical range of the groove, at which time the drive The spring is increasingly prestressed by the resulting translational movement of the impact piston until the guide element reaches the curved end of the groove. The percussion piston then moves impulsively in translation under the action of the restoring force of the drive spring towards the impact surface of the percussion head, and the guide element passes through the return groove area and returns again to the curved tip of the groove. This repeats in cycles, occurring every 360' of piston rotation. Other advantageous machine turning features correspond to the features of claims 9 to 14, each of which corresponds to claim 1.
There are various structural implementation variations of the described technical teachings. [Example] Preferred embodiments of the present invention will be illustrated. Other advantageous details of the invention can be seen from these drawings. The machine of figure l has two parts 6, 1 which are fastened together.
and 6.2 and housing 6 with embolus 6.4. A drive motor 7 is mounted between the embolus 6.4 and a shoulder 43 formed in the inner wall 16 of the housing. Conduits 8 and 9 are provided for energy supply. This is a conduit for hydraulic or pneumatic working media or electrical energy.
The rotary drive 2 includes a drive motor 7, a drive shaft 1l and, in this example, an impact piston 1 and a curved drive 3, which are rotatably mounted. The drive shaft 11 is rotatably coupled to the motor 7 on the one hand, and engages the curved drive 3 in a rotary coupling with an axial play on the other hand. This means, for example, that the shaft 11 engaging in the bore 24 of the percussion piston 1 is formed with an axially sliding projection and the bore 24 is formed with a groove for the axial projection, so that these elements are axially aligned with respect to each other. This can be achieved by being coupled so that they can slide in one direction but are not rotatable with respect to the other. A drive spring 17 is installed between the motor 7 and the rear end of the impact piston 1. The percussion piston l has a guide member 4 cut into its cylindrical circumference, into which a guide element 12, which projects radially inwardly from the housing wall 16, engages. This guide plate 4 has a helical region 4.1 over an angle of approximately 360° and a groove region 4.2 connecting its front end L3 and rear end 14. The groove is essentially straight and spirally inclined in the axial direction or steeply at a slight angle.

During one rotation of the percussion piston 1 in a clockwise direction as viewed towards the drive shaft l1, the piston is screwed back against the spring by an axial distance between the leading end 13 and the trailing end 14 of the groove. Now, as soon as the guide element 12 reaches the rear groove end 14, the drive spring 1
7 rapidly advances the impact piston 1 and hits the impact surface 15 of the impact head 18. The guide element 12 then passes through the return region 4.2 of the groove axially from the rear end 14 to the front end 13. This process is repeated periodically for every full 360° rotation. When the width of the groove return area 4.2 is insufficient to ensure the constant continuation of the rotary movement of the piston at high speeds of the impact piston 1 rapidly advancing towards the impact surface 15, the groove return area 42 is tilted steeply. It is also possible to form it in a spiral shape. Corresponding to advantageous embodiments known from the state of the art,
In the embodiment i of the invention illustrated in FIG. 3l on the housing end part 6.3. A trailing shaft 19 is attached to the rear end of the percussion head 18, by means of which the percussion head 18 is connected with the percussion piston 1 in rotational connection on the one hand and with axial clearance on the other hand. The percussion head 18 itself can be fitted with a rock perforation cap or a stepped carbide metal insert 18.1. The working stroke of the percussion head l is limited by the pitch of the helical range 4.1 of the curved groove 4. However, the piston stroke is rotated by the drive shaft l1 so as to act synchronously and in the same direction on several curved drives 3, 1, 3.2, as shown in FIGS. 2 and 4, corresponding to the embodiment. They are joined together with a play in the axial direction,
Each curvilinear drive 3.1.3.2 is subject to a separate drive spring 17.1.17.2 in order to provide a widening range. In the embodiment shown in FIG. 2, a cylindrical insert 32 is mounted in the intermediate housing part 6.2, which is also axially slidable but non-rotatably mounted in the housing part 6.2. There is. This insert is supported by a drive spring 17.2. This insert has a helical guide surface 5 whose front and rear ends are connected to each other by an axial surface section. The drive shaft 1l has a radial guide element 12.2, which slides on the helical guide surface 5 during the rotation of the shaft 11, pushing the insert 32 against the restoring force of the springs 17,2. and push it back toward the motor 7. The impact piston 1.1 has a helical groove 4.1 at its rear. A guide element 12.1 mounted on the insert 32 engages this. A drive spring 17. between a collar 44 directed radially inwardly from the front end of the intermediate housing part 6.2 and the shoulder 3.4 of the percussion piston 1.1. l is provided as a return element and an impact energy storage part. The helical ring 41 of the percussion piston 1.1 and the guiding element 12 engaged therewith. 1 forms a curvilinear drive 3.1, while the helical guide surface of the insert 32 together with the guide elements 12, 2 of the shaft 11 embodies a second curvilinear drive 3.2. The two curvilinear drives 3.1 and 3.2 are connected to each other by a drive shaft 11 so that they operate synchronously and in the same direction.
When the drive shaft 11 rotates through 360°, the translational retraction stroke of the insert 32 on the one hand and of the percussion piston 1.1 on the other hand adds up to an enlarged total piston stroke. In this structure, a perforation 24 is provided at the rear of the impact piston 1.1.
．． 1, in which a drive shaft 1l is introduced, on the one hand, non-rotatable, and on the other hand, with an axial thrust corresponding to the enlarged retraction stroke of the impact piston 1.1. In addition, corresponding elements of the machines shown in Figures 1 to 8 are given the same symbols. In the embodiment of the machine according to FIG. 3 there is a percussion piston 1.2 which can be driven into rotary motion by means of a rotary connection with a drive shaft 11.
A blind hole 20 is formed in its front region and an impact surface 15.1 is formed at its base. It has a central impact tool with an intermediate flange 45 on the impact head 18. A chisel 18.2 is movable axially forward from the flange, and a tabet 2 is movable rearward.
l is extended. The central percussion tool is mounted axially movably in the percussion head 18 and is supported with a clearance in the direction of the percussion piston 1.2 by a return spring 38.
The tabet 2l of the central impact tool enters the blind hole 20 and in the position shown in FIG. Impact surface 15. of the blind hole of the impact piston 1.2. It is in contact with 1. A helical end guide surface 5.2 is formed in the wall region 30 surrounding the blind hole 20. An insertion piece 37 is attached between a shoulder 46 provided on the inner wall surface of the housing 6 and the rear end surface of the impact head 18, and there is a guide projection 22 that abuts the impact piston 1.2 in the axial direction. Impact piston 1.2
When the shock piston 12 rotates clockwise as viewed from the motor 7, the impact piston 12 is unscrewed against the return force of the drive spring 17. As soon as this has now reached the end of the pitch of the helical guide surface 5.2, under the action of the restoring force of the spring 17 the piston 1.2 advances rapidly and its impact surface 15. 1 corresponds to the end surface 21.1 of the tabet 21. At that time, the piston moves the central impact tool to the third position against the return force of the return spring 38.
I launched it forward to the position shown in the diagram and followed it.1
8, 2 receives a driving impulse with strong force and high impact energy in order to break up a block of stone, for example.

In the embodiment shown in FIG. 4, two rigid curvilinear drives 3.1 and 3.2 are used to enlarge the working stroke of the percussion piston 1.3.
cooperate synchronously and in the same direction. In this case, the percussion piston 1.3 has an axial guide groove 23 into which a guide projection 25 mounted on the inner housing wall 16.1 engages. This guides the percussion piston 1.3 non-rotatably in the housing 6 with a floating axial movement. Furthermore, the percussion pistons 1, 3 have a central borehole 24 for the drive shaft 11. l and a rotatable tabet 21 rotatably connected thereto. There are 24.2 of 6 for 1. The chisel has two radially projecting guide projections 22.2. mounted on it at an axial distance. 22.3, which cooperates with the helical guide surface 5.1 of the percussion piston 1.3 to form a curved drive 3.1 and, on the other hand, the insert piece 3.
Cooperation with information screen 5.2 of 7. to form the curved drive section 3.2. In the embodiment of the invention shown in FIG. 4, when the drive shaft 1l and the tappet 21.1 with the guide projections 22, 222.3 on it and 6 rotate counterclockwise as seen from the side of the motor 7; , and impact piston 1 to it and 6
．． 3 is screwed back by an axial translational distance of both pitches of the helical curve 5, l and 5.2, against the return force of the drive spring 17, until the guide projection reaches the axially retracted surface of the curved path. ．． Next, impact piston 1.3 moves forward rapidly and tappet 2
The impact tool 18.3 of the impact head 18 is driven with the force of impact against the impact tool 1.1. FIG. 5 shows a simplified embodiment of the machine,
There is only one curve drive section 3.1. Other than that, the structure is similar to that of the machine shown in Fig. 4, and the curve drive section 3
．． The axial return surface of No. 1 is marked with the symbol 33, l. Figure 6 shows a machine whose internal structure is basically the same as that of the machine shown in Figure 5. Unlike that, there is no motor 7 built into the housing 6. The motor is located outside the machine and is connected to the machine in a power transmission manner by means of a transmission shaft 10 and a drive shaft 11 cooperating with it in a rotational connection. A clutch 29 is advantageously provided in the area of the housing plugs 6, 4 to connect the transmission shaft 10 with the drive shaft 1l. As a result of moving the drive motor from the housing 6 to a location outside the machine, a longer construction space is available overall for the percussion piston 1.3 and the drive spring 17 in the longitudinal direction of the housing 6. Correspondingly, without changing the overall length of the machine, the length of the percussion piston 13 and thus also its kinematic mass can be increased, for example compared to the construction of FIG. Impact energy will be generated. However, on the other hand, the overall length of the machine could be made shorter than the structure shown in Figure 5. The structure shown in Figure 6 further has the advantage of reduced manufacturing costs and, in some cases, overall weight reduction. The machine can additionally be fitted with guide surfaces 36.36.1. The machines shown in Figures 1 to 6 are constructed so that their drive is unidirectional, forward only. Figures 7 and 8 show the structure of an impact excavator in which the machine can be controlled to switch from forward to backward. Coincidentally, there are two percussion pistons 1.4, 1.5 of antipodal arrangement for advancing and retracting the machine. These are held in their respective end positions by drive springs 17.4 mounted between them. A curvilinear drive 35 is assigned to the forward percussion piston 1.5, while a curvilinear drive 3.4 is subordinate to the retraction percussion piston 1.4. They are designed in such a way that, depending on the direction of rotation of the drive shaft l1, only one of the percussion pistons 1, 4.1.5 can be excited or driven into the working stroke in each case. That is, by reversing the direction of rotation of the drive motor 7, the direction of impact of the machine is reversed. In the machine shown in FIG. 7, this reversal is achieved in that the drive shaft 11 is divided into two drive shaft sections 11.4 and 11.5. Shaft section 11.4 to shaft section 11.5
Torque transmission to the motor takes place via a rotationally orientable clutch 27 via an axial clutch surface 40. When the shaft section 11.4 rotates counterclockwise as seen from the side of the drive motor 7, the shaft section 11.5 rotates against the axial clutch surface 4.
With the cooperation of o, it is accompanied by a rotational coupling, and also rotates the tabet 21.5 with the rotational coupling. The axial guide protrusion 22.5 provided thereon slides over the guide surface 5.5 while rotating by 36 degrees each time, and the impact piston 1
．． 5 is moved toward the drive motor 7 by the pitch of the spiral guide surface 5.5 until it reaches the end of the drive curve. Next, the fifth
and corresponding to the functional details of the embodiment of FIG. 6, the drive spring 1
7.4, here its impact surface 15, 5
Hit the end face 21.6 of tabet 21.5 and push the machine forward in the direction of arrow 41. At this time, the freewheel 26 of the impact piston 1.4 acts and the piston 1.4 remains immobile. In other words, there is no rotational coupling, and the seventh
It remains at the end position shown in the figure. As soon as the direction of rotation of the shaft part l1, 4 is reversed, clockwise as seen from the drive motor 7, the freewheel 26 is closed, thus entraining the impact piston 1.4 in rotational connection and the clutch 40 on the one hand. prevents simultaneous rotation of shaft portion 11.5. Thereby, the percussion piston 1.5 causing the forward drive remains stationary in the end position shown, while the percussion piston 1.4 for the reverse stroke rotates. The guide surface 5.4 of the traverse drive 3.4 then slides against the fixed guide projection 22.4 and moves the piston in translation in the direction of the percussion head 18, and the drive spring 17.4 Prestress can be applied while accumulating impact energy. When reaching the end of the curve, the piston 1.4 returns towards the drive motor 7 and hits the end face of the coupette 214 with its impact surface 15.4. Under the action of the impact energy of the rearwardly directed percussion piston 1.4, the machine moves backwards, opposite to the forward direction. The structure of the machine shown in FIG. 8 shows the possibility of controlling the reversal of the driving direction by means of 14 and 1.52 percussion pistons arranged at opposite distances. In this case, each of the curved drives 3.4 and 3.5 has one free-running groove area 28, 428, 5. These are respectively opened at the tips of the helical guide grooves 4.4 and 4.5 and extend in the circumferential direction of the corresponding impact pistons 1.4 and 1.5. Guide grooves 4.4, 4.5 and free running grooves 28 that open tangentially at their tips. 4. 28. 5 are engaged by guide elements 12.4 and 12.5. These are mounted on cylindrical inserts 324 to 3245 which have a switching function and are slidable in the axial direction by the width of the groove. These inserts are each supported against the restoring force of control springs 42.4 to 42,5. The control functions of the inserts 32.4, 32.5 and the guide elements 12.4.12.5 attached to them are as follows: The drive shaft l1 is aligned in a counterclockwise direction when viewed from the drive motor 7 side. If, on the contrary, it is assumed that the percussion piston 1.4 rotates according to the arrow 47, the guide element 12.4 of the percussion piston 1.4 always remains in the area of the free running groove 28.4, and the percussion piston 1.4 therefore continues to rotate, but in the translational direction. It remains unmoving. On the other hand, in the curvilinear drive 3.5 the control springs 42,5
The restoring force of the spring acts to push the insert 32.5 elastically in the direction of the percussion tool 18 and, as a result of the axial movement of the insert 32.5, the guide element 12.5 attached to the insert.
5 is directed towards the helical curve of the guide 4.5 and thus comes into engagement with it, by means of the now curved drive 3.5 the rotating piston is moved against the restoring force of the spring 17. The guide element returns towards the motor and, as reiterated above, reaches the return range of the groove 4,6 after reaching the end of the guide 4,5.
When moving forward rapidly, the collision surfaces 15 and 5 hit the end surfaces of the cupettes 2l and 5. If the direction of rotation of the shaft 1l is reversed and rotated clockwise as seen from the motor 7 side, following the arrow 48, the impact piston 15 will have its guide element in the free running range of 18.5. By stopping, the percussion piston 1., despite being rotated simultaneously due to the rotational connection to the shafts 11 and 6, remains at its end without performing a percussion stroke; on the contrary, the percussion piston 1. 4 is mounted movably in the axial direction by the width of the groove, the guide element 12.4 of the insert 32.4.
enters the helical groove region 4.4 of the curved drive 3.4 and carries out the percussion movement caused by the rotation of the corresponding percussion piston 1.4 causing its percussion movement to take place in the manner described above. ．． In this way, the function is accomplished in a manner opposite to that described in 6 above. In this machine construction, the rear part of the housing 6 is closed by a separate motor housing 6.5, the end face of which
This limits the large range of internal diameter required for the cylindrical insert 32.4 and its control spring 42.4. Similarly, the large area of the inner diameter for the accommodation of the insert 32.5 and the control spring 42.5 is closed off by a flange 35 at the front of the machine.

Since the axial lengths of the impact pistons 1.4 and 1.5 are different, the impact energy generated in the forward direction of the longer impact piston is greater than that in the backward retraction direction. Double impact piston 1. 4. 1, 5. by means of a similar configuration of the aforementioned control element for the dynamically opposed, counter-pedal arrangement of and the respective operating method upon reversal of direction of the drive shaft l1, as well as mounted between the two impact pistons. The common drive spring 17 results in a relatively uncomplicated construction of the counter-drive machine.

[Brief explanation of the drawing]

FIG. 1 shows a longitudinal section through a machine with a percussion piston with a helical guide groove; FIG. 2 shows a further embodiment with two curved drives cooperating in series to increase the piston stroke 3 shows a further embodiment of the percussion piston with a helical guide surface; FIG. 4 also shows a longitudinal section of the machine; FIG. Figure 5 shows an embodiment of the machine with a second curvilinear drive mounted in series for increasing the piston stroke; 6 is a longitudinal sectional view showing a machine of another construction with shaped guide surfaces; FIG. 6 shows the machine of FIG. FIG. 7 is a vertical cross-sectional view showing an embodiment of a machine equipped with two pistons and capable of switching from forward to reverse, and FIG. 8 is a diagram showing two mutually independent drives for forward and reverse. 2 is a longitudinal sectional view showing a variant of a machine capable of switching from forward to reverse, with a piston capable of switching; FIG. 1... Impact piston, 2... Rotation drive unit, 3...
- Curved drive section, 4... Spiral guide groove, 5... Spiral guide surface, 5.2... End guide surface, 6... Housing, 6.1-6.2... Housing Part, 6.3... Same end, 6.4... Same embolus, 7... Motor,
8... Inlet pipe, 9... Discharge pipe, 1
0...Transmission shaft, 11...Drive shaft, 12...
・Guide element (protrusion), 13...Guide groove tip 14・
...Same end, 15...Collision surface, 16...Housing wall, 17...Piston drive spring, 18...Impact head, 18.2...Chisel, l9
... Accompanying axis, 20... Blind hole, 21... Tappet, 2]. 1.21.6... Tabet end face, 22... Guide projection, 23... Guide groove, 24... Drilling hole,
25... Guide projection, 26... Freewheel, 27... Clutch, 28... Free running groove, 2
9... Clutch, 30... Wall range,... Head spring, l... Return guide surface, 5... Flange, 7... Insertion piece, 40... Clutch surface, 2... - Control spring, 4... Collar 6... Shoulder, 8... Arrow. 2... Insert body 4... Shoulder part, 6... Guide surface, 8... Return spring work... Arrow, 3... Shoulder part, 5... Intermediate flange, 7... Arrow, 3 others

Claims (1)

[Scope of Claims] 1. A self-propelled impact excavator, particularly for soil drilling, comprising an impact head capable of applying an impact impulse by an impact piston attached to the propulsion side of a cylindrical housing; The piston is capable of driving a pulsating reciprocating stroke by an energy carrier that can be fed into the excavator, and as an impact piston drive unit,
A self-propelled impact excavator characterized in that a spring (17) that is periodically tensioned and relaxed is used. 2. Impact excavator according to claim 1, characterized in that the drive (2) consists of a motor (7) mounted in a housing (6). 3. Impact excavator according to claim 1 or 2, characterized in that the rotary drive section (2) comprises at least one curved drive section (3) which can be driven by the rotary drive section (2). 4. The percussion piston (1) according to claim 3, characterized in that the percussion piston (1) is formed as part of the curved drive part (3) with a helical guide groove (4) or a helical guide surface (5). impact excavator. 5 The motor (7) is designed as a hydraulic motor and has an inlet pipe (8) for a hydraulic energy carrier, preferably pressurized water.
) and the discharge pipe (9) are each connected to one piece. 6. The rotational drive unit (2) is equipped with a motor external to the rotation drive unit (2),
6. According to any one of claims 3 to 5, characterized in that it is connected in a rotary and force-transmitting manner to the curved drive (3.1) via a preferably flexible transmission shaft (10). Impact excavator as described. 7 The rotary drive unit (2) has the housing center line (X-X)
There is a drive shaft (11) provided in the drive shaft (11), which is rotatably coupled to the motor (7) or transmission shaft (10) on the one hand, and rotatably coupled to the curved drive section (3) with an axial play on the other hand.
) The impact excavator according to any one of claims 3 to 6, characterized in that the impact excavator engages with the excavator. 8. The percussion piston (1) is connected to the drive shaft (11) by a rotational connection on the one hand and freely movable in the axial direction on the other hand, and cuts into its cylindrical circumference in a helical manner with a thread-like pitch. Claim 1, characterized in that there is a guide groove (4), with a guide element (12) projecting radially inwardly from the housing wall (16), formed and arranged to engage therewith. 8. The impact excavator according to any one of 3 to 7. 9. The guide groove (4) has a helical area (4.1) with an angle of approximately 360° and a return groove area (4.2) joining its front end (13) and rear end (14), the latter 9. Impact excavator according to any one of claims 3 to 8, characterized in that the is formed essentially linearly in the axial direction or in the form of a spiral with a steep inclination at a slight angle. 10 The impact piston (1) has a drive spring (1) which is provided at its end opposite the impact surface (15) to act as an energy store during its recoil and return.
Claims 2 to 9 characterized in that they are supported by 7).
An impact excavator as described in any one of the above. 11. Claims 1 to 10 characterized in that the percussion piston (1) and the percussion head (18) are connected via a trailing shaft (19) on the one hand in a rotary connection and on the other hand with axial play. An impact excavator as described in any one of the above. 12 The impact piston (1.1) is equipped with two curved drive parts (3.1, 3.2) that are arranged in front and back in series in the operating direction in the housing (6), and these are synchronized. The curved drive parts (3.1, 3.2) each have one drive shaft (11) which is rotatably coupled to the drive shaft (11) while acting in the same direction. 4. Impact excavator according to claim 3, characterized in that drive springs (17.1, 17.2) are provided. 13 The impact piston (1.2), which can be driven into rotational motion by rotational connection with the drive shaft (11), has an impact surface (15.1) at its base.
) is formed with a blind hole (20) which also has an impact head (1
8) has a tappet (21) that can enter into the blind hole (20).
The wall region (30) of the percussion piston (1.2) surrounding the blind bore is designed with a helical end guide surface (5.2), and the percussion head (18) has an axial direction. A guide lug (22) facing the percussion piston (1.2) is mounted on the rim, the latter as well as the guide surface (5.2) being connected to the curved drive (
4. Impact excavator according to claim 3, characterized in that it is configured to cooperate as part of 3.1). 14 The impact piston (1.3) has an axial guide groove (2
3), which is engaged by a guide protrusion (25) provided on the inner wall of the housing (16.1) to move the piston (1.3).
) is non-rotatably guided with axial free travel, and the percussion piston (1.3) has a central bore (24) for the drive shaft (11).
．． 1, 24.2) and a rotatable tappet (21.1) which is rotationally connected to this shaft and which, via a radially projecting guide projection (22.1) attached to it, Claim 3 characterized in that together with the helical guide surface (5.1) of the piston (1.3), it forms a curved drive (3.1).
Impact excavator as described. 15. There are two percussion pistons (1.4, 1.5) in antipodal arrangement for the advancement or retraction of the device, which are controlled at both ends by a drive spring (17.4) mounted between them. It is held in position and the associated curve drive (3.4
, 3.5) have means (26, 27, 28) by means of which, depending on the direction of rotation of the drive shaft (11), only one percussion piston (1.4 or 1.5) is in the working stroke. The impact excavator according to any one of claims 1 to 4, wherein the impact excavator is capable of being excited or driven. 16 As a rotational direction control means, a curved drive section (3.4,
3.5) or the freewheel (26) or two shaft parts (1.
1.4, 11.5) or an impact piston (1
．． 16. Any one of claims 1 to 15, characterized in that the free running groove ranges (28.4, 28.5) of the guide grooves (4.4, 4.5) of the guide grooves (4, 1.5) are formed. One of the mentioned impact excavators. 17. Impact excavator according to any one of claims 1 to 16, characterized in that the impact head (18) is mounted axially movably in the housing.